EP1333176A1

EP1333176A1 - Swash or wobble plate compressors

Info

Publication number: EP1333176A1
Application number: EP02002383A
Authority: EP
Inventors: Daniel c/oZexel Valeo Compressor Damson; Otfried c/oZexel Valeo Compressor Schwarzkopf; Michael c/oZexel Valeo Compressor Arnemann
Original assignee: Zexel Valeo Climate Control Corp
Current assignee: Valeo Thermal Systems Japan Corp
Priority date: 2002-01-31
Filing date: 2002-01-31
Publication date: 2003-08-06
Anticipated expiration: 2022-01-31
Also published as: EP1333176B1; DE60230714D1

Abstract

A swash or wobble plate compressor comprises at least one piston (1) moveable in a cylinder (3) and a swash or wobble plate arrangement (8) rotatable mounted between the piston (1) and a drive shaft. An at least part-spherical bearing (6) is attached to the piston (1) against which the swash or wobble plate arrangement (8)acts to reciprocate the piston (1) in the cylinder (3). In order that the effects of wear caused by lateral forces are mitigated the centre (12, 18) of the bearing (6) is located at a position (20) offset with respect to a longitudinal plane in which both the longitudinal axis (7) of the piston (1) and a longitudinal axis (9) of a drive shaft for the piston (1) lie. This means that the centre (12,18) of the bearing (6) is offset both radially with respect to the longitudinal axis (7) the piston (1) and in a selected direction of rotation of the swash or wobble plate arrangement (8) in a compressor with respect to the piston (1).

Description

The present invention relates to a swash or wobble plate compressor, in particular a compressor for a vehicle air-conditioning system, and to piston for use in such a compressor.
As illustrated diagrammatically in Fig. 1, a conventional swash or wobble plate compressor comprises a piston 1 with a piston head 2 at one end which reciprocates in a cylinder bore 3. The end 4 of the piston 1 opposite the piston head 2 extends out of the cylinder bore 3 and is provided with a recess 5 in which is mounted a part-spherical bearing 6 that is centrally disposed with respect to the longitudinal axis 7 of the piston 1. A swash or wobble plate arrangement 8, which is rotatably driven by a drive shaft (not shown) of the compressor, is connected to the bearing 6 so that drive forces are transmitted from the arrangement 8 via the bearing 6 to the piston 1. As the swash or wobble plate arrangement 8 is inclined with respect to the longitudinal axis 9 of the drive shaft, the forces transmitted to the piston 1 are not exclusively axial forces but comprise a substantial radial component F_Q, which is dependent on the angle of inclination of the plate arrangement 8. The radial component F_Q results in forces of reaction F_A and F_B, which cause contact to occur between the piston 1 and the cylinder bore 3 that leads to wear in bore 3 and consequent compression and wear of the piston 1.
The object of the present invention is to provide a swash or wobble plate compressor in which the effects of wear caused by lateral forces are substantially mitigated.
According to a first aspect of the present invention there is provided a compressor comprising at least one piston moveable in a cylinder, a drive shaft, a swash or wobble plate arrangement rotatable mounted between the piston and the drive shaft, an at least part-spherical bearing attached to the piston against which the swash or wobble plate arrangement acts to reciprocate the piston in the cylinder, and characterised in that the centre of the bearing is located at a position offset with respect to a longitudinal plane in which both the longitudinal axis of the piston and a longitudinal axis of a drive shaft for the piston lie.
Preferably, the centre of the bearing is located at a position offset radially outwardly with respect to the longitudinal axis of the piston.
Preferably also, the centre of the bearing is located at a position offset in the direction of rotation of the drive shaft.
Preferably also, the centre of the bearing is located at a position offset at a position located between 240° and 360° in the direction of rotation of the drive shaft. Advantageously, the centre of the bearing is located at a position offset at a position located between 270° and 360° in the direction of rotation of the drive shaft.
Preferably also, the piston defines a recess at one end in which the bearing is located.
Preferably also, the bearing comprises part-spherical pockets located on opposite sides of the recess.
Alternatively, the bearing comprises a ball attached to one end of the piston against which the swash or wobble plate arrangement acts to reciprocate the piston.
According to a second aspect of the present invention there is provided a piston for use in a swash or wobble plate compressor comprising a piston head at one end and attached at its other end to an at least part-spherical bearing against which a swash or wobble plate arrangement of a compressor can act to reciprocate the piston in a cylinder, and characterised in that the centre of the bearing is located at a position offset radially with respect to the longitudinal axis the piston and in a selected direction of rotation of the swash or wobble plate arrangement in a compressor with respect to the piston.
The present invention will now be described by way of example with reference to the accompanying drawings, in which:-
Fig. 1 is a diagrammatic, part longitudinal cross-sectional view of a piston and piston guide means forming part of a conventional driving mechanism of a swash or wobble plate compressor;
Fig. 2a is a diagram showing the forces acting on a piston in a conventional swash or wobble plate compressor;
Fig. 2b is a diagram showing the forces acting on a piston in a swash or wobble plate compressor according to the present invention;
Fig. 3 is a diagram showing a piston and piston guide means forming part of a first embodiment of swash or wobble plate compressor according to the invention;
Fig. 4 is a diagram similar to Fig. 3 but of a second embodiment of compressor;
Figs. 5a is a diagram showing the location of lateral forces acting around the circumference of a conventional piston during its operation and the length of its stroke;
Fig. 5b is a diagram showing graphically the lateral forces projected onto the contact length of the piston during its stroke; and
Fig. 5c is a diagram showing graphically the lateral forces acting on the piston during its stroke.
In all the drawings, the same components or components with the same function have been given the same reference numeral.
As described above with reference to Fig. 1, in a swash or wobble plate compressor forces are transmitted to the piston 1 that are not exclusively axial forces but comprise a substantial radial component F_Q dependent on the angle of inclination of the swash plate arrangement 8. These radial or' lateral forces cause wear to occur in the cylinder bore 3 and on the piston 1.
With reference to Figs. 2a and 2b, it will be demonstrated that if the centre of a bearing arrangement such as the centre of a shoe pocket of a piston of a compressor is arranged off-axis, an opposite moment is introduced into the piston which offsets the aforesaid forces F_A and F_B. Wear between the piston and the cylinder is thereby reduced.
Figs. 2a and 2b are diagrams of a cross-section through piston 1 with a bearing 6 and swash or wobble plate arrangement 8. The radial force F_Q is shown that is dependent on the angle of inclination of the arrangement 8 and this is resolved into the lateral forces of reaction F_A and F_B,
It can be seen that in the conventional arrangement shown in Fig. 2a, the lateral force F_Aa can be determined as follows:- FAa * a = FQ *(a+b) ∴FAa = FQ * a+b a
However, in the arrangement according to the invention shown in Fig. 2b, the lateral force F_Ab differs by virtue of the offsetting of the centre of the bearing 6 from the longitudinal axis 7 of the piston 1 by the distance e. In this case the lateral force F_Ab is determined as follows:- FAb * a = FQ * (a+b)- FT*e ∴FAb = FQ * a+b a - FT * e a Where

F_G: is the gas force of the compressor
F_T: is the resultant of the gas force
F_Q: is the radial force
F_A and F_B: are the resultant forces of the radial force
e: is the distance of the off-axis shift of the centre of the bearing
a: is the length of the piston between the points of application of the resultant forces F_A and F_B
b: is the distance between the points of application of the forces F_B and F_Q

The ratio of F_Aa to F_Ab is therefore as follows:- FAa FAb = FQ * a+b a FQ * a+b a - FT *e a
Hence
It can thus be seen that, all other forces being equal, the lateral force F_Ab must be less than the lateral force F_Aa. It should be appreciated that for the purposes of these calculations it has been assumed that the force F_B does not generate a moment, the pivot point being taken at the point of intersection of the central pivot axis and the point of application of F_B. All other forces were determined accordingly.
F_B will increase in the embodiment according to the invention shown in Fig. 2b because a moment F_T*e is introduced. F_B will therefore increase by the reaction moment. However, the increase in this resultant force can be tolerated because the most damaging wear caused by lateral forces occurs at the end of the piston opposite the piston head 2 and at the corresponding end of the bore 3. Very little, if any, wear is ever found at the piston head 2 and the closed end of the bore 3. Hence, it is not expected that a slight increase in the force F_B will cause significant increased wear.
It will be appreciated that offsetting of the centre of the bearing 6 from the longitudinal axis 7 of the piston 1 by the distance e does not reduce the forces acting on the piston 1 overall but the advantage is that their points of application are shifted to locations where they are, in part, internally compensated for within the piston body and, where any transmitted to the cylinder bore 3, it is at locations less damaging to operation of the compressor as a whole than would otherwise be the case. These locations are in areas which are subjected to less stress and are distributed in a better way. The effects of wear caused by lateral forces are therefore substantially reduced.
The offsetting of the centre of the bearing 6 radially outwardly from the longitudinal axis 7 of the piston 1 can be carried out in any swash or wobble plate compressor.
In a first exemplary embodiment as shown in Fig. 3, a wobble plate arrangement 8 comprises a double-slide arrangement in which the bearing 6 comprises a pair of part-spherical sliding shoes 10 between which a swash or wobble plate 8 is located. The shoes 10 are mounted between two pressure-bearing shoe pockets 11 defined respectively on opposite sides of the recess 5, each of the pockets 11 defining a part-spherical bearing surface. The centres 12 of the pocket surfaces are located at a position offset radially' outwardly with respect to the longitudinal axis 7 of the piston 1.
In a second exemplary embodiment as shown in Fig. 4, at the end of the piston 1 opposite the piston head 2 is a bearing 6 comprising a ball 13 with a spherical working surface around which is located a washer 14 and retainer 15 connected via a bearing 16 to the swash or wobble plate arrangement 8. The arrangement 8 also comprises a pressure-bearing shoe 17 which bears against the part-spherical end surface portion of the ball 13 to transmit force to the piston 1. As before, it can be seen that the centre 18 of the surface portion of the ball 13 is located at a position offset radially outwardly with respect to the longitudinal axis 7 of the piston 1.
In addition to the centres 12 and 18 of the part-spherical surfaces of the bearings 6 for the piston against which the swash or wobble plate arrangements 8 bear being offset radially with respect to the longitudinal axis 7 of the piston 1, it is also advantageous if the centres 12 and 18 are offset with respect to a longitudinal plane in which both the longitudinal axis 7 of the piston 1 and the longitudinal axis 9 of the drive shaft for the piston 1 lie.
Figs. 5a, 5b and 5c show the circumferential lateral forces running around a conventional piston and the length of its path of contact during the piston stroke. These determine the amount of wear caused by the lateral forces and hence can be used to determine the preferred position for the location of the centres 12 and 18 of the bearings 6.
With reference to Fig. 5a, at top dead centre OT the length of the piston contact area is maximal, whereas at the lower dead centre UT it is minimal. Now, if the circumferential lateral force is projected onto the contact length, as shown in Fig. 5b, it is clear that for a lengthened support area of the piston, or a correspondingly lengthened cylinder face, the following priority sequence results: D, A, B, C. That is, in position C the imposed load is least and between positions A and C the imposed load rises to its maximum at position D. Preferably, therefore, the location of the centre 12 or 18 of the bearings 6 should be offset to counter the higher levels of the force in the direction of rotation at an offset position located between 240° and 360° in the direction of rotation of the drive shaft, such as at the positions 19 and 20 marked with an 'x'. Position 19, which lies at 360° is simply a translation of the point of contact radially with respect to the longitudinal axis 7.of the piston. Advantageously, however, a position 20 is selected which lies is between 270° and 360° in the direction of rotation of the drive shaft and which is offset with respect to a longitudinal plane in which both the longitudinal axis 7 of the piston 1 and a longitudinal axis 9 of a drive shaft for the piston 1 lie.
It will be appreciated that Fig. 5a does not indicate the direction in which the swash or wobble plate arrangement 8 is turning. Depending on its direction of rotation, in Figs. 5b and 5c there will be a mirror-image reflection of the paths about the x or horizontal axis.
It will also be appreciated that during the manufacture of a piston in accordance with the present invention that in order for the position 20 for the centre of the bearing 6 to be selected at an offset position located between 240° and 360°, the direction of rotation of the swash or wobble plate arrangement 8 within the compressor with respect to the piston 1 will have had to have been decided.

Claims

A compressor comprising at least one piston (1) moveable in a cylinder (3), a drive shaft, a swash or wobble plate arrangement (8) rotatable mounted between the piston (1) and the drive shaft, an at least part-spherical bearing (6) attached to the piston (1) against which the swash or wobble plate arrangement (8)acts to reciprocate the piston (1) in the cylinder (3), and
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (20) offset with respect to a longitudinal plane in which both the longitudinal axis (7) of the piston (1) and a longitudinal axis (9) of a drive shaft for the piston (1) lie.
A compressor as claimed in Claim 1,
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (20) offset radially outwardly with respect to the longitudinal axis (7) of the piston (1).
A compressor as claimed in Claim 1 or Claim 2,
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (20) offset in the direction of rotation of the drive shaft.
A compressor as claimed in any of Claims 1 to 3,
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (20) offset at a position located between 240° and 360° in the direction of rotation of the drive shaft.
A compressor as claimed in any of Claims 1 to 3,
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (20) offset at a position located between 270° and 360° in the direction of rotation of the drive shaft.
A compressor as claimed in any of Claims 1 to 5,
characterised in that
the piston (1) defines a recess (5) at one end in which the bearing (6) is located.
A compressor as claimed in Claim 6,
characterised in that
the bearing (6) comprises part-spherical pockets (11) located on opposite sides of the recess (5).
A compressor as claimed in any of Claims 1 to 5,
characterised in that
the bearing (6) comprises a ball (13) attached to one end of the piston (1) against which the swash or wobble plate arrangement (8) acts to reciprocate the piston (1).
A piston (1) for use in a swash or wobble plate compressor comprising a piston head (2) at one end and attached at its other end to an at least part-spherical bearing (6) against which a swash or wobble plate arrangement (8) of a compressor can act to reciprocate the piston (1) in a cylinder (3), and
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (21) offset radially with respect to the longitudinal axis (7) the piston and in a selected direction of rotation of the swash or wobble plate arrangement (8) in a compressor with respect to the piston (1).
A piston (1) as claimed in Claim 9,
characterised in that
the centre (12, 18) of the bearing (6) is located at a position offset radially outwardly with respect to the longitudinal axis (7) of the piston (1).
A piston as claimed in Claim 9 or Claim 10,
characterised in that
the centre (12, 18) of the bearing (6) is located at a position (21) between 240° and 360° in the selected direction of rotation for the piston (1).